Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/0224—Non-manual adjustments, e.g. with electrical operation
  • B60N2/02246—Electric motors therefor
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/0224—Non-manual adjustments, e.g. with electrical operation
  • B60N2/02246—Electric motors therefor
  • B60N2/02253—Electric motors therefor characterised by the transmission between the electric motor and the seat or seat parts
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
  • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
  • B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
  • B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
  • B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
  • B60N2/225—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms
  • B60N2/2252—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable by cycloidal or planetary mechanisms in which the central axis of the gearing lies inside the periphery of an orbital gear, e.g. one gear without sun gear
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H1/00—Toothed gearings for conveying rotary motion
  • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
  • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
  • F16H13/02—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members without members having orbital motion
  • F16H13/04—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members without members having orbital motion with balls or with rollers acting in a similar manner
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
  • F16H13/10—Means for influencing the pressure between the members
  • F16H13/12—Means for influencing the pressure between the members by magnetic forces

Definitions

• the invention relates to a gear stage, in particular a vehicle seat, with the features of the preamble of claim 1.
• the invention is based on the object to improve a gear stage of the type mentioned. This object is achieved by a gear stage with the features of claim 1.
• Advantageous embodiments are the subject of the dependent claims.
• the gear stage according to the invention is based on the same basic principle as the known gear stage.
• the translation can be adjusted by contours on the drive and / or output, for example by a groove within which the ball is running.
• the transmission stage of the invention improves the properties with respect to translation, efficiency and low noise and clamps as desired, the rotor always radially, whereby the disadvantages described are eliminated, especially the noise in EC drives with rotors low mass and the low efficiencies of high-gain, single-stage differential gears be avoided.
• Per desired drive direction is preferably exactly one rolling element, for example a roller, but preferably a ball, provided in order to avoid over-determination. If only one drive direction is required, only a single ball or a single other rolling elements is necessary.
• the gear stage according to the invention is preferably used in an actuator for a vehicle seat, for example, a backrest tilt adjuster, a height adjuster or a tilt adjuster.
• the actuator comprises a drive motor and the gear stage according to the invention and, for example, drives a load-absorbing gear, as disclosed in DE 10 2004 019 466 B4, which forms a component of the inherently movable seat structure.
• the actuator may optionally have a second or further gear stages, which are connected downstream of the first gear stage according to the invention and upstream of the load-picking gear.
• the load-bearing gearbox can perform a rotational movement or a linear movement or a superposition of both movements.
• the actuator may also be formed as an actuator or drive such, for example, rotate a cable drum, which winds a rope for unlocking. Inserts outside a vehicle seat are also conceivable, for example with window regulators and adjustable mirrors.
• Fig. 1 shows a cross section of the first gear stage, the sake of clarity, only one ball and right outside whose radial load representation is located.
• FIG. 6 shows a cross section of the first gear stage with magnets as pressing elements
• 7 is a schematic side view of a vehicle seat in a rear row of seats
• An actuator 1 for a vehicle seat 3 has a housing 5 and a drive motor 7 arranged in the housing 5.
• the housing 5 is usually multi-part, but formed with as few parts as possible.
• the present case designed as an EC internal rotor motor drive motor 7 comprises a rotor 8 which is rotatably mounted about a first axis A in the housing 5 and which carries permanent magnets, and an electronically commutated stator 9.
• the bearing of the rotor 8 in the housing. 5 takes place by means of two designed as a rolling bearing rotor bearing 8a.
• the actuator 1 also has a first gear stage 10 which comprises a drive 12 rotatable about the first axis A and a driven output 14 rotatable about a second axis B parallel thereto, which are each mounted in the housing 5.
• the present annular drive 12 is preferably designed in one piece with the rotor 8 of the drive motor 7 and thereby roller-mounted in the housing 5 by means of the rotor bearing 8a. But it is also a derte training of rotor 8 and drive 12 with suitable coupling and a separate storage in the housing 5 possible.
• the present also annular output 14 is mounted in the housing 5 by means of a likewise designed as a rolling bearing output bearing 14a.
• first axis A and the second axis B are spaced apart from one another by an eccentricity e, in that the rotor bearings 8a and the output bearing 14a in the housing 5 are fixedly arranged relative to one another.
• the second axis B is moved upwards relative to the first axis A. The position of the eccentricity e is thus spatially fixed with respect to the housing 5.
• the smaller diameter drive 12 is disposed radially inward and the larger diameter driven output 14 is disposed radially outward.
• the power transmission between the drive 12 and the output 14 takes place in the present embodiment as Reibradgetriebeeck means of at least one ball 15 (or another rolling element), which is arranged between the drive 12 and output 14, where between the drive 12 and output 14, a curved, wedge-shaped free space forms, briefly referred to as a wedge gap.
• the ball 15 is automatically clamped in the direction of this wedge gap (in the illustration of FIG. 1 in a clockwise direction), then rotates about its own axis and thus drives the output 14 stocky at.
• exactly one ball 15 (or another rolling element) is provided between the drive 12 and the output 14 for each drive direction, each of which (with the exception of the direction of rotation) having the same effect,
• the output 14 is provided on the - radially inwardly facing - effective surface with a contour, such as a groove or V-shaped groove or the like, within which the ball 15 runs while rolling on sloping walls.
• a contour such as a groove or V-shaped groove or the like
• the output radius of the ball 15 can be reduced, even set smaller than the drive radius, and thus the reduction ratio can be influenced.
• the use of a V-shaped groove on the drive and a cylindrical surface on the output can be translated quickly. This is - in addition to the direct transmission of radial forces - the advantage of a Reibradgetriebewel over a gear transmission stage.
• the described first gear stage 10 can be used with fixed position eccentricity in any combination with other gear stages.
• the actuator 1 has a second gear stage 20.
• the first gear stage 10 serves as a feed stage for the output side arranged second gear stage 20th
• the second gear 20 is presently designed as a toothed eccentric planetary gear.
• a drive shaft 21 rotatable about the second axis B supports by means of a first eccentric portion 21a and a second eccentric portion 21b axially displaced along the second axis B two pinions 22a and 22b preferably offset by 180 ° and arranged in two planes.
• Both the first pinion 22a and the second pinion 22b which are preferably of the same design, are externally toothed and mesh with an internal toothing of the housing 5 which has a number of teeth greater by at least one relative to the pinions 22a and 22b.
• the pinions 22a and 22b Upon rotation of the central and fixed to the output 14 connected to the drive shaft 21, the pinions 22a and 22b perform a rolling movement on the housing 5.
• the pinions 22a and 22b act by means of bolts and holes on a common, designed as a hollow shaft output shaft 24, which then also rotates.
• the drive shaft 21 and the output shaft 23 are concentric with the second axis B, so that ultimately the drive motor 7 is arranged offset to the two-stage gear assembly from first gear stage 10 and second gear stage 20 in total to the eccentricity E, which fix in position and amount of the common housing 5 is predetermined.
• the rather high number of rolling bearings in Fig. 2 serves to increase the overall efficiency.
• the annular output 14 of the first gear stage 10 and the associated designed as a double eccentric drive shaft 21 of the second gear stage 20 in one piece as a sleeve with all required ball rolling grooves and preferably produce this by chipless forming and Kalibriervoncie.
• Fig. 3 is intended to illustrate this.
• the balls 15 are pressed or pulled by the one or more pressing elements 31 in the wedge-shaped gap and thereby simultaneously pressed against drive 12 and output 14.
• the ball 15 with its acting at an angle to each other forces ultimately ultimately ultimately a Klemmrollen- or here Klemmkugelkeratilauf.
• the freewheel is a self-switching coupling. In operation, i. During the drive movement, therefore, only that ball 15, which is further moved by the drive 12 into the wedge-shaped gap, will remain in contact with both the drive 12 and the output 14. The opposing ball 15 for the opposite drive direction is moved out of the wedge gap assigned to it, in spite of contact pressure element 31, and then loses the double contact.
• Fig. 8 shows a transmission variant which operates with only one, in this case magnetically biased ball 15.
• the actuator 1 with this first gear stage 10 is integrated in a serving as backrest inclination fitting. If, in the position shown in Fig. 7, the backrest 35 is unlocked electrically at its upper edge, and then pivots forward, i. in Fig. 7 counterclockwise, the output 14 in Fig. 8 also rotates counterclockwise, keeps in contact with the drive 12 and thus drives the rotor 8 at.
• the rotor 8 either with no or a precisely controlled braking torque can be applied, for example, to define a maximum swing speed or just before the end of the possible angle of motion deliberately slow down the movement.
• Fig. 9 shows an arrangement in which both balls 15 can be switched independently of each other in a passive and an active position.
• a restraint device 37 provided (here a simple geometry with very weak magnet).
• the retaining device 37 positions the ball 15 in the rest position so that it has no contact with the drive 12 and / or output 14 (ie at least one or optionally two components), whereby in the rest position drive 12 and output 14 are completely decoupled from each other.
• two separate and separately switchable electromagnets are provided as pressing elements 31 which, when activated, attract the respectively assigned ball 15 and thus close the frictional connection for this respective direction of movement. Since the ball contact forces required for higher torques set automatically due to the wedge effect during operation, these energies require minimal energies, which only have to provide "loose" contact with the start of the movement.
• the electromagnets used as contact elements 31 can consequently be de-energized during operation ,
• control forks 41 are used, of which only one is shown.
• Such a control fork 41 can be controlled externally.
• the controlled control forks 41 bring the balls 15 respectively into active (in the wedge gap) or passive (out of the wedge gap) positions and thus enable the drive motor 7 decoupled to allow, for example, a manual quick adjustment or emergency operation, as before in connection with Figs. 7 and 8 is described.
• FIG. 11 A further advantageous embodiment of a coupling function is shown in Fig. 11, in which a drive 12 comprehensive, at three points to this standing in slight frictional contact ball guide ring 43 can be seen, which leads the ball 15.
• the ball guide ring 43 due to the weak frictional contact to the drive 12 tends to always move the ball 15 within the free space in the drive direction of the rotor 8 try (ie in the wedge gap) and thus in the engaged state itself, as well as the ball 15th to maintain its angular position.
• the ball 15 is - pivoted from their previous contact - pivoted to the opposite side.
• the resulting saving of a second ball 15 is less important than the fact that with this arrangement without further active control elements or magnets, the transmission can be completely disengaged by the rotor 8 (and thus the drive 12) after completion of the drive movement by a known angle (in the illustration of FIG. 11 about 80 ° counterclockwise) is rotated back.
• This makes it possible to relieve tension in the entire actuator 1 controlled, and allows, for example, an enclosure of the drive or driven bearings with an elastomeric ring to reduce the structure-borne noise or for the purpose of targeted control of the elastic displacements of the transmission elements in operation under load.
• a side effect is to be noted here that such a design also allows the use of non-magnetic ball materials such as ceramic or plastic.
• FIG. 12 A conceivable embodiment with a housing 5 which is provided with deliberately different bearing stiffnesses, Fig. 12. With these - depending on the spatial directions - different bearing stiffness, for example, the radial forces can be reduced. In the present case, it is a modification of the embodiment of FIG. 11. Particularly when thermoplastic materials are used as the housing material, it is advisable to disengage the first gear stage 10 in order to minimize material creep over longer downtimes at high temperatures.
• FIG. 13 shows a stepped inner contour of the output 14.
• balls 15 of different sizes are in contact with this inner contour.
• these translation stages can be switched by disengaging the one ball 15 and engaging the other ball 15.
• movement direction dependent power and torque requirements are frequently the case.
• a suitable translation for each direction of rotation can be installed.
• more than two gear ratios can be installed.
• the contact geometries of the drive 12 can of course also be defined in the same sense, or one or more outputs can be used 14 (or drives 12) are arranged axially one above the other or two different contours on the output 14 (or drive 12) may be provided. Instead of the balls 15 and other rolling elements may be provided.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Aviation & Aerospace Engineering (AREA)
• Transportation (AREA)
• Chairs For Special Purposes, Such As Reclining Chairs (AREA)
• Gear Transmission (AREA)
• Transmission Devices (AREA)
• Seats For Vehicles (AREA)
• Friction Gearing (AREA)
• Retarders (AREA)

Priority Applications (7)

Applications Claiming Priority (2)

Publications (1)

Family

ID=39327413

Family Applications (3)

Family Applications After (2)

Country Status (9)

Families Citing this family (15)

Citations (4)

Family Cites Families (31)

• 2007
  • 2007-11-16 KR KR1020107011276A patent/KR101394918B1/ko not_active IP Right Cessation
  • 2007-11-16 DE DE102007056390A patent/DE102007056390B4/de not_active Expired - Fee Related
  • 2007-11-16 WO PCT/DE2007/002118 patent/WO2009052771A1/de active Application Filing
  • 2007-11-16 CN CN2007801012201A patent/CN101835656B/zh not_active Expired - Fee Related
  • 2007-11-16 US US12/739,252 patent/US8435150B2/en active Active
  • 2007-11-16 DE DE102007056392A patent/DE102007056392A1/de not_active Withdrawn
  • 2007-11-16 RU RU2010119572/11A patent/RU2476740C2/ru not_active IP Right Cessation
  • 2007-11-16 EP EP07866206.1A patent/EP2200862B1/de not_active Not-in-force
  • 2007-11-16 DE DE102007056391A patent/DE102007056391B4/de not_active Expired - Fee Related
  • 2007-11-16 JP JP2010530266A patent/JP5319687B2/ja not_active Expired - Fee Related
  • 2007-11-16 DE DE112007003746T patent/DE112007003746A5/de not_active Withdrawn
• 2008
  • 2008-10-17 EP EP08842208.4A patent/EP2200864B1/de not_active Not-in-force
  • 2008-10-17 WO PCT/DE2008/001766 patent/WO2009052813A1/de active Application Filing
  • 2008-10-17 JP JP2010530273A patent/JP5485158B2/ja not_active Expired - Fee Related
  • 2008-10-17 PL PL08842208T patent/PL2200864T3/pl unknown
  • 2008-10-17 US US12/739,269 patent/US20110037306A1/en not_active Abandoned
  • 2008-10-17 CN CN200880112849.0A patent/CN101835657B/zh not_active Expired - Fee Related
  • 2008-10-17 RU RU2010119571/11A patent/RU2499695C2/ru not_active IP Right Cessation
  • 2008-10-17 WO PCT/DE2008/001765 patent/WO2009052812A1/de active Application Filing
  • 2008-10-17 KR KR1020107011277A patent/KR101391309B1/ko not_active IP Right Cessation

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